A modular apparatus for water production

ABSTRACT

A modular apparatus ( 10 ) for water production from atmospheric air comprises: a first parallelepiped module ( 200 ) provided with an inlet opening ( 21 ) for moist air, an outlet opening ( 22 ) of the dehumidified air, a ventilator ( 23 ), configured such as to force an air flow to cross an internal volume of the first module ( 200 ) from the inlet opening ( 21 ) to the outlet opening ( 22 ), a condensation unit ( 20 ), located internally of the first module ( 200 ) so as to intercept the air flow, and a collecting tub ( 291, 292, 293 ) located inferiorly of the condensation unit ( 20 ) for collecting the condensation water that is separating from the air flow; and a second parallelepiped module ( 300 ) in which a refrigerating unit ( 30 ) is contained provided with at least a portion of a refrigerating circuit ( 31 ) in which a refrigerating fluid circulates and an evaporator in which the refrigerating liquid evaporates so as to cool the air flow internally of the condensation unit ( 20 ); where the first module ( 200 ) and the second module ( 300 ) are fixed to one another at a respective interconnecting fact and where the second module ( 300 ) exhibits a side of the interconnecting face having a width (W) equal to twice a width (W/2) of a side of the interconnecting face of the first module ( 200 ).

TECHNICAL FIELD

The present invention relates in general to production of potable waterfrom the atmospheric air, more in particular to an apparatus forproduction of potable water from atmospheric air loaded with moisture atambient temperature.

BACKGROUND

As is known, for production of water, for example potable water, inplaces where the water supply sources are poor or difficult to reach,apparatus are used for obtaining a quantity of water, for examplepotable water, from dehumidification of the atmospheric air.

These known-type apparatus generally comprise a casing, for example abox casing, in which are arranged, in special predefined spaces, atleast a condensation unit able to be crossed by a flow of ambient air,possibly pre-cooled, which is essentially constituted by a heatexchanger defining an evaporator for a cooling fluid circulating in anappropriate refrigerating circuit, provided, apart from with theabove-mentioned evaporator, with a condenser thereof and an expansionvalve.

Further, there is a place internally of the casing for the motor foractivating the compressor and also for a water purification unit of thecondensation water produced by the condensation unit.

These apparatus, especially when the water flow rate is of a relevantentity, exhibit a very voluminous casing, which during the design stageand during the assembly stage, must be predisposed for correct andrational positioning of the operating units which enable production ofwater.

A drawback encountered in these apparatus of known type is that they arepoorly flexible to variations of the needs for production capacity ofwater, for example, once the apparatus has been installed in theworkplace, should there be a change in demand of water quantity, forexample a demand for double the production of water with respect to whatthe apparatus was initially designed for, in order to satisfy the newdemand it is necessary to completely change the layout of the productionunits and/or dimension them so that they are contained and rationallyarranged internally of a new casing having modified dimensions.

Further, even the realizing of these apparatus requires a greater amountof labor and a design that is customized each time for the most rationaland effective arrangement of the production units internally of thecasing, with an increase in production costs of the user's plant and,over time, of the amortisement costs for the buyer.

Not least, a drawback encountered in the apparatus of known type lies inthe fact that it is particularly complicated to transport the apparatusfrom the place of production to the place of use, the location whereofcan sometimes be in difficult places to reach, and where the maneuveringspace is substantially small.

An aim of the present invention is to obviate the above-mentioneddrawbacks in the prior art, with a solution that is simple, rational andrelatively inexpensive.

The aims of the invention are attained by the characteristics recited inthe independent claim. The dependent claims delineate preferred and/orparticularly advantageous aspects of the invention.

SUMMARY

A modular apparatus (10) for production of water from atmospheric airwhich comprises:

a first parallelepiped module provided with an inlet opening for moistair, an outlet opening of the dehumidified air, a ventilator, configuredsuch as to force an air flow to cross an internal volume of the firstmodule from the inlet opening to the outlet opening, a condensationunit, located internally of the first module so as to intercept the airflow, and a collecting tub located inferiorly of the condensation unitfor collecting the condensation water that is separating from the airflow; and

a second parallelepiped module in which a refrigerating unit iscontained, provided with at least a portion of a refrigerating circuitin which a coolant fluid circulates, and an evaporator in which thecoolant fluid evaporates so as to cool the air flow internally of thecondensation unit;

wherein the first module and the second module are fixed to one anotherat a respective interconnecting face and wherein the second moduleexhibits a side of the interconnecting face having a width W that istwice a width W/2 of a side of the interconnecting face of the firstmodule.

With this solution, it is possible to configure the apparatus so thatthe arrangement of the operating units is more rational and efficientwith respect to apparatus of known type, with a reduction in productioncosts which are reflected in the buying cost of the plant of the userand, therefore, in the amortisement time of the apparatus for the buyer.

Further, the times and costs of labor for assembly of the apparatus aregreatly reduced, and the transportation costs of the apparatus areoptimized.

In a further aspect of the invention, the outlet opening is realized atthe interconnecting face of the first module and the inlet opening canbe made at an opposite face to the interconnecting face of the firstmodule.

With this solution, the dehumidified and cold air that exits the firstmodule is forced to enter directly into the second module, contributing,for example, to optimizing the functioning of the refrigerating circuit,for example contributing to the cooling of the condenser of therefrigerating circuit.

In a first embodiment of the invention, the apparatus can comprise athird parallelepiped module in which a water purification unit of thecondensed water is contained, configured so as to source the water fromthe collecting tube, wherein the third module and the second module arefixed to one another at a respective interconnecting face and whereinthe second module exhibits a side of the interconnecting face having awidth W that is twice a width W/2 of a side of the interconnecting faceof the third module.

With this solution, the apparatus can produce potable water and at thesame time the arrangement of the operating unit of the layout of theapparatus is optimized.

For the same aims illustrated above, a contiguous face to theinterconnecting face of the third module is further provided with a sideexhibiting a length L equal to a length L of a side of a contiguous faceto the interconnecting face of the first module, the first module andthe second module being reciprocally flanked and fixed by means of therespective contiguous faces.

In a further embodiment of the invention, the apparatus can comprise athird parallelepiped module in which a water purification unit of thecondensed water is contained, configured so as to source the water fromthe collecting tube, wherein the third module and the second module arefixed to one another at a respective interconnecting face and whereinthe second module exhibits a side of the interconnecting face having awidth W that is equal to the width W of a side of the interconnectingface of the third module.

With this solution, the apparatus can produce potable water and at thesame time the arrangement of the operating unit of the layout of theapparatus is optimized.

In this further embodiment, for example, the apparatus can comprise apair of the first modules flanked and fixed reciprocally by means of arespective contiguous face to the interconnecting face, respectivelyfixed to the interconnecting face of a second module of a pair of thesecond modules fixed to one another by means of an opposite face withrespect to the respective interconnecting face.

With this solution, the water flow rate produced by the apparatus can bedouble with respect to the flow rate produced by the embodimentdescribed in the foregoing, while maintaining a rational and compactapparatus layout.

In a variant of the above-described further embodiment, for example, theapparatus can comprise two of the pairs of the first modules and two ofthe pairs of the second modules, wherein the access openings of thefirst modules of a first pair of first modules are symmetricallyopposite the access openings of the first modules of the second pair.

With this solution, the water flow rate produced by the apparatus can bedouble with respect to the flow rate produced by the first variant ofthe further embodiment described in the foregoing, while maintaining arational and compact apparatus layout.

In both the variants of the further embodiment, the refrigerating unitof each of the second modules is provided with a respective branch ableto cross a respective condensation unit located in a first module of thefirst modules.

In both the variants of the further embodiment, the outlet openings ofone or the first modules comprises an accelerator element of thedehumidified air flow which exits from the outlet opening.

In this way the dehumidified and cold air that exits from each firstmodule can reach the respective second module, even when the secondmodule is further away.

A pair of heat exchangers, of which a first heat exchanger and a secondheat exchanger, are advantageously contained in each first module,respectively located upstream and downstream of the condensation unit inthe crossing direction thereof by the air flow, the pair of heatexchangers being connected by means of a hydraulic circuit comprising arecycling pump of a liquid contained in the hydraulic circuit.

With this solution, the air entering from the inlet opening and directedto the heat exchange plate can be pre-cooled, before arriving at theheat exchange plate, making the production of water thereby moreefficient; further, the cold air exiting from the heat exchange planecrosses the second heat exchanger, which has the double function ofrendering heat to the dehumidified air, so as to keep the liquidcontained in the hydraulic circuit at a low temperature, and to functionas a coalescent membrane for the small drops of condensation watertransported by the air flow beyond the heat exchange plate.

The refrigerating circuit advantageously comprises a compressor of thecooling fluid moved by a motor, a condenser of the cooling fluid locateddownstream of the compressor in the circulating direction of the coolingfluid in the refrigerating circuit, an expansion valve locateddownstream of the condenser, and the evaporator of the cooling fluid.

The condensation unit, preferably the heat exchange plate, is theevaporator of the refrigerating circuit.

Further, with the aim of improving the layout of the apparatus, thecondenser can comprise a dissipating fan located on an upper face of thesecond module, one of the lateral faces contiguous to theinterconnecting face of the second module exhibiting an access openingfor the ambient air.

The size of the access opening, the ventilator and the dissipating fanare advantageously configured so as to define an air mixturesubstantially comprising ⅔ of ambient air entering the second modulefrom the access opening and ⅓ of dehumidified air entering the secondmodule by means of the ventilator.

With this air ratio in inlet to the second module, the performance ofthe refrigerating unit can be optimized.

The motor is advantageously an electric motor.

With this solution the noise level of the apparatus can be reduced and,for example, it is possible to electrically supply the motor by means ofphotovoltaic panels, with undoubted advantages in economic terms.

The first module can be provided with a filter able to intercept theinlet opening.

For example the purification unit can comprise at least ananti-particulate filter and a mineralizer.

BRIEF DESCRIPTION OF THE DRAWINGS

Further characteristics and advantages of the invention will emerge froma reading of the following description, provided by way of non-limitingexample with the aid of the figures illustrated in the appended tablesof drawings.

FIG. 1 is an axonometric view of a first embodiment of an apparatusaccording to the invention.

FIG. 2 is a view from above of FIG. 1.

FIG. 3 is a section view along line III-III of FIG. 2.

FIG. 4 is a frontal elevation of FIG. 1.

FIG. 5 is a section view along line V-V of FIG. 3.

FIG. 6 is a section view along line VI-VI of FIG. 3.

FIG. 7 is a section view along line VII-VII of FIG. 3.

FIG. 8a is an axonometric view of a first embodiment of a condensationunit according to the invention.

FIG. 8b is an axonometric view of a second embodiment of a condensationunit according to the invention.

FIG. 9 is a view from above of FIG. 1.

FIG. 10 is an view from above of a second embodiment of the apparatusaccording to the invention.

FIG. 11 is a view from above of a third embodiment of the apparatusaccording to the invention.

FIG. 12 and FIG. 13 are hydraulic diagrams of the apparatus according tothe invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

With particular reference to the figures, reference numeral 10 denotesin its entirety an apparatus for production of water, for examplepotable water, from the atmospheric air laden with moisture, which isable to obtain a quantity of water by condensation of the moisturepresent in the atmospheric air. The apparatus 10 is able, for example,to obtain from 2.5 m³ of water a day to 10.0 m³ of water a day, instandard atmospheric conditions, i.e. at ambient temperature of 30° C.and relative humidity of 70%.

The apparatus 10 comprises a condensation unit 20 configured forcondensing a quantity of water present in the atmospheric air.

The condensation unit 20 comprises an inlet opening 21 in which themoist air to be dehumidified enters, and an opposite outlet opening 22from which the dehumidified air exits.

The condensation unit 20 comprises at least a ventilator 23, which forexample is located at the outlet opening 22, and is configured so as toforce an air flow to enter through the inlet opening 21 and exit fromthe outlet opening 22.

The condensation unit 20 comprises a heat exchange plate 24, which isinterposed between the inlet opening 21 and the outlet opening 22, so asto intercept the air flow and able to be crossed by the air flow.

The heat exchange plate 24 comprises a first parallelepiped body 240arranged with the main dimension vertical and provided with a front face241, with respect to the advancement direction of the air flow from theinlet opening 21 to the outlet opening 22, and an opposite rear face242.

The front face 241 and the rear face 242 are for example rectangularwith a vertical longitudinal axis.

Between the front face 241 and the rear face 242 the firstparallelepiped body 240 defines a through-channel 243 that is open atthe faces 241,242, which crosses the first parallelepiped body 240 inthe direction, perpendicular to the faces 241, 242, that the ventilator23 imposes on the air flow entering from the inlet opening 21. Thethrough-channel 243 is closed in the transversal direction (laterally,inferiorly and superiorly), so that the air flow can be directed only inthe longitudinal direction along the through-channel, entering the firstparallelepiped body 240 itself from the front face 241 and exitingtherefrom only from the rear face 242.

The first parallelepiped body 240 is crossed transversally, with respectto the crossing direction of the air flow imposed by the ventilator 23,by a first tube bundle 244, for example bent in a serpentine shape so asto cross the whole transversal section of the first parallelepiped body240 several times and, for example, extending over the whole height andfor the whole thickness thereof. In this way, the first tube bundle 244is lapped by the air flow crossing the heat exchange plate 24.

The first parallelepiped body 240, like the tube bundle 244, is made ofa metal material having high heat conductivity and being resistant tooxidation, such as for example stainless aluminum, of a type suitablefor use with food.

The condensation unit 20 comprises a pair of heat exchangers 25,26,which are interposed between the inlet opening 21 and the outlet opening22 and are able to be crossed in series by the air flow which is forcedby the ventilator 23.

In practice, the condensation unit 20 comprises a first exchanger 25located upstream of the heat exchange plate 24, in the crossingdirection thereof by the air flow, and a second exchanger 26, locateddownstream of the heat exchange plate 24.

The heat exchange plate 25,26 comprises a second parallelepiped body250,260 arranged with the main dimension vertical and provided with arespective front face 251,261, with respect to the advancement directionof the air flow from the inlet opening 21 to the outlet opening 22, andan opposite rear face 252,262.

Each front face 251, 252 and each rear face 252, 262, is for examplerectangular, with the longitudinal axis vertical and having a like shapeto the faces 241, 242 of the first parallelepiped body 240.

Between the front face 251,261 and the rear face 252,262 of each secondparallelepiped body 250,260 are defined respective through-channels253,263 (entirely alike to the ones shown in the first parallelepipedbody 240), which are open at the faces 251,252, 261,262 and cross therespective second parallelepiped body in the direction, perpendicular tothe faces, that the ventilator 23 imposes on the air flow entering fromthe inlet opening 21. The through-channels 243 are closed in thetransversal direction (laterally, inferiorly and superiorly), so thatthe air flow can be directed only in the longitudinal direction alongthe through-channels 253, 263, crossing each second parallelepiped body250,260 entering the second parallelepiped body 250, 260 from the frontface 251,261 and exiting therefrom only from the rear face 252,262.

Each second parallelepiped body 250,260, is for example made of a metalmaterial having high heat conductivity and being resistant to oxidation,such as for example stainless aluminum, of a type suitable for use withfood.

The inlet opening 21 of the condensation unit 20 is defined by the frontface 251 of the second parallelepiped body 250 which defines the firstexchanger 25 and the outlet opening 22 is defined by the rear face 262of the second parallelepiped body 260 defining the second exchanger 26.

The condensation unit 20 further comprises a filter apparatus 27 which,located so as to intercept the inlet opening 21 and occupying all theair passage surface, is able to be crossed by the whole moist air flowwhich enters the inlet opening 21, i.e. in the front face 251 of thesecond parallelepiped body 250, so as to remove any solid particulateand/or any pollutant and/or any saline residues and/or other impurities.

In the illustrated example, the filter apparatus 27 comprises inparticular one or more first filters 271, for example of theanti-particulate type, downstream of which one or more second filters272 can be present, for example of the rigid pocket type. Upstream ofthe first filters 271, the filter apparatus 27 can also include thepresence of a protection grid 273.

A chemical air treatment unit 275 can be included between the filterapparatus 27 and the condensation unit 20, as illustrated in FIGS. 8aand 8 b.

This chemical treatment unit 275 is useful as the ambient air cancontain contaminants having variable composition both in terms of thenatural climatic and biological alterations (organic putrefaction,volcanic eruptions etc.) and due to the anthropic presence deriving fromcivic and industrial activity such as extraction industries, petroplants, craft workshops and agricultural activities (animal husbandry oruse of fertilizers, disinfectants, phyto-pharmaceutical products,herbicides, etc.) which cause diffusion of micro-pollutants which aredispersed in the air.

The micro-pollutants can belong to various categories, among which:Ammoniac, Volatile Organic Compounds (hydrocarbons in various forms:Aliphatics, Aromatics, Halogenates, etc.) cations and anions in ionicform or saline form (Potassium, Hydrogen Sulphide, Nitrogen Oxide, etc.)or Aerosols in general containing elements and dissolved moleculesbelonging to the above-indicated families of compounds.

The chemical treatment unit 275 reduces the concentration of themicro-pollutants before the air flow crosses the condensation unit 20,so that at most a minimal quantity thereof is left in the water, thusfacilitating the successive steps of purification and potabilization. Inpractice, the chemical treatment unit 275 protects and prevents thecontamination of the whole condensation unit.

The chemical treatment unit 275 can comprise, for example, anair-permeable membrane, which occludes the inlet 21 of the condensationunit 20 so as to intercept all the air flow directed internally andeliminate the concentration of micro-pollutants.

The permeable membrane can be for example crossed by only Zeolite (forexample carbalite and/or phillipsite) so as to realize a step ofzeolitic catalysis, or by only activated charcoal, so as to realize anadsorption step of the micro-pollutants.

Alternatively, the permeable membrane might be made from a mixture ofZeolite and activated charcoal, so as to carry out both steps and obtaina better elimination of the airborne micro-pollutants. Should thepresence of contaminants be particularly high, it is possible to includeinstallation in series of one or more permeable membranes made ofZeolite, activated charcoal or mixtures thereof according to thetreatments to be made.

In practice, the treatment unit 275 might comprise a container or aseries of containers, in box or cylinder form, containing theabove-mentioned permeable membranes, which can be arranged parallel toone another in order to be crossed in series by the air flow, and eachof which can be composed of or will contain the suitable materials forthe treatment to be carried out, i.e. Zeolite, activated charcoal or amixture thereof. These containers are preferably structured in such away as to be easily removed from the structure, so that a replacement ofthe porous membranes can be made with fresh or regenerated ones.

In the example, the heat exchange plate 20 comprises a plurality ofventilators 23 located posteriorly of the rear face 262 of the secondheat exchanger 26, with respect to the advancement direction of the airflow from the inlet opening 21 to the outlet opening 22.

The ventilators 23 are such as to occupy the whole passage surface ofthe air on the rear face 262 of the second exchanger 26, in practicebeing uniformly distributed with respect to the surface of the rear faceitself.

In the example, the ventilators 23 are flanked and aligned to oneanother along a vertical direction, i.e. along the prevalent extensiondirection of the outlet opening 22 and of the heat exchange plate 24.

Each second parallelepiped body 250, 260 is crossed transversally, withrespect to the crossing direction of the air flow imposed by theventilator 23, by a respective second tube bundle 254,264, for examplebent in a serpentine shape so as to cross the whole transversal sectionof the second parallelepiped body 240 several times and, for example,extending over the whole height and for the whole thickness thereof. Inthis way, the second tube bundle 254,264 is sprayed by the air flowcrossing the heat exchange 25, 26.

The heat exchangers 25, 26 and in particular the second tube bundles254, 264 thereof are connected to one another by means of a hydrauliccircuit 255 provided with a recycling pump 256 able to recycle a heatexchange liquid, for example water, in the hydraulic circuit 255 andthen between the second tube bundles 254, 264. For example, thehydraulic circuit 255 is a closed circuit.

The second tube bundles 254,264, are for example made of a metalmaterial having high heat conductivity and being resistant to oxidation,such as for example stainless aluminum, of a type suitable for use withfood.

The hydraulic circuit 255 can comprise a first portion 257 whichconnects the inlet of the second tube bundle 254 of the first exchanger25 with the outlet of the second tube bundle 26 and a second portion 258which connects the outlet of the second tube bundle 254 of the firstexchanger 25 with the inlet of the second tube bundle 264 of the secondexchanger 26.

In practice, the heat exchange liquid present in the hydraulic circuit255 circulates, by means of the thrust exerted by the recycling pump256, and in succession crosses the second tube bundle 264 of the secondexchanger 26, where it is cooled by the dehumidified air flow whichexits from the heat exchange plate 24, the first portion 257 (cold), thesecond tube bundle 254 of the first exchanger 25, in which by exchangingheat with the moist air flow it pre-cools the air flow andcorrespondingly heats up, and the second portion 258 (hot).

In some embodiments it is possible to use the heat of the cold heatexchange liquid circulating in the first portion 257, entirely or onlyin part (if in a quantity of lower than the total in circulation) forcooling a second liquid of a further hydraulic circuit 265, for exampleclosed, in which the heat exchange liquid circulates, destined to servea user, for example the water of a cooling plant or the like.

In practice, the further hydraulic circuit 265 comprises a first branch267, provided with a respective opening and closing valve, whichbranches from the first portion 257, and a second branch 266, alsoprovided with a respective opening and closing valve, which enters thesecond portion 258 in an injection point downstream of the branchingpoint of the first branch 267 in the exchange liquid flow directionalong the second portion 258.

A heat exchanger can be included between the first branch 267 and thesecond branch 266, for example of a liquid-liquid type, used for coolinga liquid of an appropriate user.

The heat exchange plate 24, the first heat exchanger 25 and the secondheat exchanger 26 are arranged in succession and aligned in a pack, sothat the rear face 262 of the second parallelepiped body 260 defines theoutlet opening 22 of the condensation unit 20, while the front face 251of the first parallelepiped body 250 defines the inlet opening 21.

The heat exchange plate 24 is advantageously fixed by means of threadedorgans to the pair of heat exchangers 25,26, so as to define a compactsandwich structure.

The threaded organs, for example, can be stud screws 28 having axesparallel to the advancement direction of the air flow from the inletopening 21 to the outlet opening 22.

In practice, the stud screws 28 exhibit a length only slightly greaterthan the sum of the thicknesses of the heat exchangers 25,26 and theheat exchange plate 24 and exhibit threaded opposite ends, able toproject out of the sandwich structure (see FIG. 8a ).

Each stud screw 28 is insertable in a series (in the example four innumber located at the vertices of the front faces 241,251,261 and of therear faces 242,252,262) of through-holes 280 (see figure FIGS. 5-7), forexample completed by hollow tubular elements, aligned with one anotherand realized in the heat exchange plate 24 and in the pair of heatexchangers. The opposite ends of the stud screws 28 are screwed to locknuts 281 able to block the sandwich pack structure constituted by theheat exchange plate 24 and the pair of heat exchanger 25,26.

Alternatively or additionally, each parallelepiped body 245,250,260comprises a perimeter flange able to border each of the front faces241,251,261 and of the rear faces 242,252,262, for example projectingexternally of the respective parallelepiped body 240,250,260.

For example, the parallelepiped bodies 240,250,260 can be coupled to oneanother by means of the respective perimeter flanges, for examplesolidly (e.g. by welding).

For example, each parallelepiped body 240,250,260 can comprise one ormore inspection windows provided with openable and/or removable caps forinspection and periodic cleaning of the parallelepiped bodies240,250,260 (as shown for example in FIG. 8b ).

In practice, the sandwich structure constituted by the firstparallelepiped body 240 and by the pair of second parallelepiped bodies250, 260 defines a tunnel, closed in a transversal direction to thefluid crossing direction imparted by the ventilators 23 and openexclusively at the inlet opening 21 (i.e. the front face 251) and theoutlet opening 22 (i.e. the rear face 262).

Downstream of the ventilators 23 an accelerator element of thedehumidified air flow can be fixed, which exits from the outlet opening.

For example, the accelerator element can comprise a converging nozzle230, i.e. a converging connection provided with a broadened endassociated to the downstream end of the ventilator 23 and a free taperedend located downstream of the advancement direction of the air flow,imposed by the same ventilator 23.

The condensation unit 20 further comprises at least a collecting tub291,292,293 located inferiorly thereof at least at the heat exchangeplate 24 for collecting the condensation water separating from the airflow which crosses the heat exchange plate.

For example the condensation unit 20 comprises a plurality of collectingtubs, of which a main tub 291 located inferiorly of the heat exchangeplate 24, a first auxiliary tub 292 located inferiorly of the firstexchanger 25 and a second auxiliary tub 293 located inferiorly of thesecond exchanger 26.

The second auxiliary tub 293, notwithstanding the fact that thecondensation function of the second exchanger 26 is substantially nil orin any case very small, collects the water that deposits on the secondexchanger, as it performs a coalescent function of coalescing andcollecting and making the smallest drops of condensate bigger, the saidsmallest drops being deposited on the first exchanger 25 and/or on theheat exchange plate 24, and being transported by the air flow towardsthe outlet opening 22, so that once made larger they fall into thesecond auxiliary tub 293.

Each collecting tub 291,292,293 is slidably associated to the respectiveparallelepiped body 240,250,260 with respect to a horizontal slidingdirection perpendicular to the advancement direction of the air flowalong the condensation unit 20.

For example, a sliding guide is included below each parallelepiped body240,250,260, for example formed by a pair of opposite profiles having aC-shaped transversal section, able to define a sliding coupling with arespective collecting tub.

For example, the connection between the parallelepiped body 240,250,260and the respective collecting tub 291,292,293 is made substantiallysealed or in any case isolated from outside by means of removable and/oropenable padding (shown for example in FIG. 8b ).

The bottom of each collecting tub 291,292,293 is inclined with respectto a horizontal plane, so as to make the water converge towards alowered collection point.

The condensation unit 20 is for example arranged internally of a firstparallelepiped module 200, i.e. an imaginary volume having aparallelepiped shape in which the condensation unit 20 is contained.

The first module 200, for example, is bordered by a tubular frame, forexample formed by rectangular portals 201 (for example two in number)parallel to one another and joined by at least four longitudinalcross-members 202 parallel to the advancement direction of the air flowimposed by the ventilator 23. For example the cross members 202 are ableto join the vertices of the portals 201.

The portals 201 exhibit a vertical longitudinal axis and have a slightlygreater dimension with respect to the faces 241,251,261; 242,252,262 ofthe parallelepiped bodies 240,250,260.

The two portals 201 are for example parallel to the faces 241,251,261;242,252,262 of the parallelepiped bodies 240, 250, 260 and,respectively, externally border the front face 251, which defines theinlet opening 21, and the rear face 262 which defines the outlet opening22.

In practice the rear face of the first module 200, i.e. the face whichborders the rear face 262 of the second exchanger 26 and is proximalthereto, defines an interconnecting face of the first module 200, theopposite face to the interconnecting face of the first module 200(bordered by the front portal 201) borders and is proximal to the frontace 251 of the first exchanger 25 and each contiguous face (for examplefour in number, of which two lateral, one upper and one lower) to theinterconnecting face of the first module 200 is bordered by a pair ofcross-members 202 parallel to one another.

The opposite face to the interconnecting face of the first module 200(and possibly also the interconnecting face itself) is provided withfiller sheets able to fill any interspace between the portal 201 and theinlet opening 21 (and, respectively, the outlet opening 22), so that theair flow forced by the ventilator 23 is totally conveyed along thetunnel defined by the sandwich structure of the heat exchangers 25, 26and the heat exchange plate 24.

Each contiguous face to the interconnecting face can be provided withfiller sheets, for example fixed sheets or mobile sheets, for example ofa hatch or door type. At least one of the filler sheets closing acontiguous lateral face is advantageously openable for removal of thecollecting tubs 291,292,293 along the sliding direction and/or forremoving, along the sliding direction, one or more of the parallelepipedbodies 240,250,260 for cleaning or replacing them.

The first module 200 exhibits a width, for example defined by theextension of a short side (horizontal) of the front portal 201, whichextension is W/2, in which W is for example a maximum width of theinternal compartment of a container of standard dimensions (for example234 cm), for example transportable by sea.

In the example W is a little smaller than the maximum width of theinternal compartment of a container of standard dimensions andpreferably is substantially 220 cm.

The length L of the first module 200, in the parallel direction to theadvancement direction of the air flow along it, can be greater than thewidth W.

The apparatus 10 further comprises a refrigerating unit 30.

The refrigerating unit 30 can be based on any known cooling technology,though in the majority of applications a conventional refrigeratingcompressing cycle of steam will be the sturdiest and most versatilesystem. For this reason, the refrigerating unit 30 generally comprises arefrigerating circuit 31 in which a refrigerating fluid circulates, forexample R-134a, through a compressor 310, a condenser 312, an expansionvalve 319 and an evaporator.

The compressor 310 is configured to increase the pressure of therefrigerating fluid to the state of vapor coming from the evaporator.The compressor 310 can be a rotary screw compressor or a compressor ofany other type. The compressor 310 is moved by a motor 311, for exampleby an electric motor connected to an electric distribution grid or agenerator. The compressor 310 might also be of type normally called“semi-hermetic”, i.e. having an electric motor inserted in thecompressor body. It is however possible for the motor 311 to be aninternal combustion engine, for example a diesel engine.

The condenser 312 is configured such as to cause condensation of thehigh-pressure refrigerating fluid coming from the compressor 310, losingheat to the external environment. The condenser 312 can be a tube and/orfin condenser, and can be provided with one or more fans 314 able tocreate a forced-air flow through the condenser 312, facilitatingdissipation of the heat produced by the condensation of refrigeratingfluid.

The pressure valve 319 is configured so as to lower the pressure of therefrigerating fluid coming from the condenser 312. The expansion valve319 can be a fixed-geometry valve or a variable-geometry valve, forexample having an electro-mechanical activation. In particular, theexpansion valve 319 can be a regulatable valve, for example athermostatic valve.

The evaporator is configured to cause evaporation of the lower-pressurerefrigerating fluid coming from the expansion valve 319, subtractingheat from the surrounding atmosphere.

In the example the evaporator of the refrigerating unit 30 is defined bythe heat exchange plate 24 of the condensation unit 20, i.e. by the tubebundle 244, so that the evaporation of the refrigerating fluid candirectly cool the environmental air flow to be dehumidified.

In practice, the tube bundle 244 defines a branch of the refrigeratingcircuit 31 which receives the refrigerating fluid in the liquid stateand at low pressure in outlet from the expansion valve 319 and sends itto the vapor state towards the compressor.

As it evaporates internally of the tube bundle 244, the refrigeratingfluid cools the air flow which, as it crosses the condensation unit 20,laps the external surface of the tube bundle 244.

It is however possible that in other embodiments the evaporator of therefrigerating unit 30 is separated from the heat exchange plate 24 ofthe condensation unit 20. For example, the evaporator of therefrigerating unit 30 can be used to cool a vector fluid, for example amixture of water and glycol, which is circulated by a further pump in anauxiliary hydraulic circuit connected with the heat exchange plate 24.In this way, in the heat exchange plate 24, the air flow is cooled bythe vector fluid and not directly by the refrigerating fluid, avoidingcontamination of the condensation water in a case of small faults in theheat exchange plates 24.

In other embodiments, the refrigerating unit 30 can also comprise afurther evaporator for cooling an air flow internally of a secondcondensation unit 20 for production of water.

In practice, this further evaporator is the heat exchange plate 24 of asecond condensation unit 20 substantially identical to the one describedin the foregoing.

The two heat exchange plates 24 of this embodiment can be connected tothe refrigerating circuit 31 so as to be arranged reciprocally inparallel with respect to the heat exchange plate 24, i.e. so that therefrigerating fluid circulating in a heat exchange plate 24 does notcirculate in the other and vice versa.

The pressure of the refrigerating fluid flowing in the further heatexchange plate 24 is regulated by a further expansion valve 319 locatedat the inlet of the heat exchange plate 24 of the second condensationunit 20, for example a further thermostatic valve.

This embodiment can be particularly useful in all cases in which theclimatic conditions or production needs can require a lowerrefrigerating power in order to obtain the condensation of the waterpresent in the air. In this case, the second condensation unit 20 can beset in function on reaching a under-exploiting condition of the powerthe compressor 310 can develop.

In some embodiments, the refrigerating unit 30 can also comprise asecond condenser 321 configured so as to enable condensation of therefrigerating fluid coming from the compressor 310. The second condenser321 can be connected to the refrigerating circuit 31 so as to bearranged in parallel with respect to the first condenser 312, i.e. sothat the refrigerating fluid circulating in the second condenser 321does not circulate in the first condenser 312 and vice versa.

In practice, the second condenser 321 can comprise an inlet for therefrigerating fluid, which is hydraulically connected by means of abranch conduit 322 to a portion of the refrigerating circuit 31comprised between the outlet of the compressor 310 and the inlet of thefirst condenser 312 and an outlet for the refrigerating fluid, which ishydraulically connected by means of a delivery conduit 323 to a portionof the refrigerating circuit 31 comprised between the outlet of thefirst condenser 312 and the inlet of the expansion valve 319.

The flow of refrigerating fluid flowing at the inlet of the secondcondenser 321 is regulated by an intercept valve 324 located in thebranch conduit 322. A further intercept valve 325 can also be positionedin the portion of the refrigerating circuit 31 comprised between theattachment point of the branch conduit 322 and the inlet of the firstcondenser 312. Each of the intercept valves 324 and 325 can be anelectrical actuating valve. Alternatively the two valves 324 and 325might be replaced by a single valve of the three-way type whichexchanges with a single activation.

In the second condenser 321 the refrigerating fluid is in heat exchangerelation with a further vector fluid, for example water or a mixture ofwater and glycol, which circulates in an auxiliary circuit 326 activatedby a pump 327. In the illustrated example, the auxiliary circuit 326comprises a storage tank 328 able to store the vector fluid, while thesecond condenser 321 is configured as an exchanger (of any type) inwhich the refrigerating fluid is able to exchange heat with the vectorfluid, with no direct contact. In other embodiments, the secondcondenser 321 might however be configured as a tube bundle immerseddirectly in the storage tank 328. In other embodiments, the secondcondenser 321 might be an exchanger in which the refrigerating fluidexchanges heat directly with the air used as a heat vector fluiddestined to other uses or to a room to be heated.

In any case the condensation of the refrigerating fluid internally ofthe second condenser 321 supplies heat to the vector fluid, whichtherefore heats up. This high-temperature vector fluid can therefore beadvantageously used for many purposes.

One of these aims, for example the aim of realizing a defrosting systemenabling thawing the ice which in determined functioning conditions thatwill be more fully clarified in the following, can form in the heatexchange plate 24 of the condensation unit 20, and also in the first andsecond exchanger 25 and 26.

For this purpose, the auxiliary circuit 326 can comprise a deliveryconduit 329 which connects an outlet of the storage tank 328 with theinlet of a further tube bundle 330, formed by one or more tube arrays,which is located internally of the first parallelepiped body 240 of theheat exchange plate 24, between the arrays of the first tube bundle 244.The auxiliary circuit 326 also comprises a return conduit which connectsan outlet of the tube bundle 330 with an inlet of the storage tank 328,passing through the pump 327 and the second condenser 321.

To extend the defrosting system also to the heat exchangers 25 and 26,the auxiliary circuit 326 can be hydraulically connected to thehydraulic circuit 255, in such a way that the hot fluid coming from thestorage tank 328 can selectively circulate also internally of each ofthe second tube bundles 254 and 264. In this way, the heat exchangeliquid circulating normally between the first and the second exchanger25 and 26 coincides with the vector fluid which circulates in theauxiliary circuit 326 and in the storage tank 328. It is howeverpossible that in other embodiments, the first and the second exchanger25 and 26 can each comprise a further tube bundle connected to theauxiliary circuit 326 independently of the hydraulic circuit 255, in asubstantially like way to what is described for the heat exchange plate24.

The refrigerating unit 30 (with the exception of the evaporator, i.e.the heat exchange plate 24) is for example arranged internally of afirst parallelepiped module 300, i.e. an imaginary volume having aparallelepiped shape in which the condensation unit 20 is contained.

The second module 300, for example, is bordered by a tubular frame, forexample formed by rectangular portals 301 (for example two in numberwhich can be defined by the rectangular portals 201 themselves borderingthe first module 200) parallel to one another and joined by at leastfour longitudinal cross-members 302 parallel to the advancementdirection of the air flow imposed by the ventilator of the first module200. For example the cross members 302 are able to join the vertices ofthe portals 301.

The portals 301 exhibit a vertical longitudinal axis and lie on parallelplanes to the faces 241,251,261; 242,252,262 of the parallelepipedbodies 240,250,260 of the condensation unit 20.

In practice, each portal 301 delimits an interconnecting face of thesecond module 300, able to interconnect, as will be more fully describedin the following, at least with the interconnecting face of a firstmodule 200.

Each contiguous face to the interconnecting face (for example four innumber of which two lateral, one upper and one lower) of the secondmodule 300 can be provided with filler sheets, for example fixed sheetsor mobile sheets, for example of a hatch or door type. At least one ofthe lateral filler sheets is advantageously openable for aspirating, bythe fans 314, air from the environment surrounding the second module.

The second module 300 exhibits a width (in a perpendicular direction tothe advancement direction of the air flow along the first module 200),for example defined by the extension of a horizontal side of the frontportal 301, which extension is W, in which W is for example a maximumwidth of the internal compartment of a container of standard dimensions(for example 234 cm), for example transportable by sea.

In the example W is a little smaller than the maximum width of theinternal compartment of a container of standard dimensions andpreferably is substantially 220 cm.

In practice, the second module 300 exhibits a width W (in thetransversal direction to the crossing direction of the first module 200by the air flow) that is twice the width W/2 of the first module.

The length L of the first module 200, in the parallel direction to theadvancement direction of the air flow along it, can be smaller than thewidth W.

The second module 300 and the first module 200 exhibit a same height,for example a maximum length of the internal compartment of a containerof standard dimensions, for example transportable by sea.

The first module 200 and the second module 300 are joined to one anotherand reciprocally fixed by means of a respective interconnecting face,which are able to match substantially parallel to one another.

In practice, the interconnecting face of the first module 200 occupies ahalf of the surface of one of the interconnecting faces of the secondmodule 300 to which it is fixed.

The interconnecting faces can be fixed to one another by bolts oranother threaded organ and/or by means of appropriate weld seams whichinterconnect the longitudinal members defining the portals 201 of thefirst module 200 and the portals 301 of the second module 300.

The dissipating fans 314 of the condenser 312 of the refrigerating unit30 are, for example, located on an upper contiguous face of the secondmodule 300.

One or both the lateral contiguous faces of the second module 300 canexhibit an access opening (closable at least partially by an openablehatch) from which the ambient air drawn from the fans 314 enters).

The width of the access opening, the rotation velocity and the overallflow rate of the ventilators 23, the rotation velocity and the overallflow rate of the dissipating fan 214 are configured so as to define anair mixture substantially comprising ⅔ of ambient air entering thesecond module 300 from the access opening and ⅓ of dehumidified airentering the second module 300 by means of the ventilator 23 and exitingfrom the first module 200.

The apparatus 10 further comprises a purification unit 40, which is ableto make the condensation water collected by the condensation unit 20potable.

The purification unit 40 comprises a sourcing pump 41 which, by means ofa tube 42, is able to collect the condensation water collected on thebottom of the collecting tub 291,292,293 and send it to a purifier 43.

The purifier 43 can be provided with one or more filters, of which forexample an anti-particulate filter, an anti-bacterial filter and/or afilter for removing the organic substance that might be present in thewater, an activated charcoal filter and/or other filter elements.

Further, the purifier 43 can comprise a sterilizer, for examplefunctioning with UV rays or ozone.

Further, the purifier 43 can comprise a mineralizer, for example locateddownstream of the filters and suitable for adding condensation waterfiltered from mineral salts or other organoleptic elements.

The purifier 43 can lastly comprise a tank 44 in which the waterpurified by the purifier 43 is stored, which tank 44 comprises anemptying stopcock 45.

The condensation unit 20 is for example arranged internally of a firstparallelepiped module 400, i.e. an imaginary volume having aparallelepiped shape in which the condensation unit 20 is contained.

The third module 400, for example, is bordered by a tubular frame, forexample formed by rectangular portals 401 (for example two in number)parallel to one another and joined by at least four longitudinalcross-members 402 parallel to the advancement direction of the air flowimposed by the ventilator 23 along the first module 200. For example thecross members 402 are able to join the vertices of the portals 401.

The portals 401 exhibit a vertical longitudinal axis and lie on parallelplanes to the faces 241,251,261; 242,252,262 of the parallelepipedbodies 240,250,260 of the condensation unit 20.

In practice, each portal 401 delimits an interconnecting face of thesecond module 400, able to interconnect, as will be more fully describedin the following, at least with the interconnecting face of the secondmodule 300.

Each contiguous face to the interconnecting face (for example four innumber of which two lateral, one upper and one lower) of the thirdmodule 400 can be provided with filler sheets, for example fixed sheetsor mobile sheets, for example of a hatch or door type.

For example, the emptying stopcock 45 is accessible from one of theabove-mentioned contiguous faces, for example lateral.

In a first embodiment shown in figures from 1 to 9, the third module 400exhibits a width, for example defined by the extension of a short side(horizontal) of the front portal 401 (in relation to the crossingdirection of the first module 200 by the air flow), which extension isW/2, in which W is for example a maximum width of the internalcompartment of a container of standard dimensions (for example 234 cm),for example transportable by sea.

As mentioned, in the example W is a little smaller than the maximumwidth of the internal compartment of a container of standard dimensionsand preferably is substantially 220 cm.

In practice, in the first embodiment, the third module 400 exhibits awidth W/2 (in the transversal direction to the crossing direction of thefirst module 200 by the air flow) that is equal to the width W/2 of thefirst module 200 and half the width W of the second module 300.

The length L of the third module 400, in the parallel direction to theadvancement direction of the air flow along the first module 200, in thefirst embodiment, is equal to the length L of the first module 200.

The third module 400 and the first module 200 exhibit a same height, forexample a maximum length of the internal compartment of a container ofstandard dimensions, for example transportable by sea.

In practice, in this embodiment, the first module 200 and the thirdmodule 300 exhibit a same external dimension and a same external shape.

The third module 400 and the second module 300 are joined to one anotherand reciprocally fixed by means of a respective interconnecting face,which are able to match substantially parallel to one another.

The interconnecting faces can be fixed to one another by bolts oranother threaded organ and/or by means of appropriate weld seams whichinterconnect the longitudinal members defining the portals 301 of thesecond module 300 and the portals 401 of the third module 400.

In practice, the interconnecting face of the third module 300 occupies ahalf (that is, in the first embodiment, the half left free by the firstmodule 200) of the surface of one of the interconnecting faces of thesecond module 300 to which the first module 200 is fixed.

A contiguous lateral face of the third module 400 is, also, fixed to acontiguous lateral face of the first module 200.

The above-mentioned contiguous lateral faces can be fixed to one anotherby bolts or another threaded organ and/or by means of appropriate weldseams which interconnect the cross members 202 and 402 defining thecontiguous lateral faces, respectively of the first module 200 and thethird module 400.

In practice, in the first embodiment, the apparatus 10 is constituted byone first module 200, one second module 300, one third module 400, fixedto one another as described above.

In a second embodiment shown in FIG. 10, in which the above-describedwater flow and the power of the apparatus 10 are substantially doublewith respect to the apparatus 10 of the first embodiment, the thirdmodule 400 exhibits a width, for example defined by the extension of ashort side (horizontal) of the front portal 401 (in relation to thecrossing direction of the first module 200 by the air flow), whichextension is W, in which W is for example a maximum width of theinternal compartment of a container of standard dimensions (for example234 cm), for example transportable by sea.

In the example W is a little smaller than the maximum width of theinternal compartment of a container of standard dimensions andpreferably is substantially 220 cm.

In practice, in the second embodiment, the third module 400 exhibits awidth W (in the transversal direction to the crossing direction of thefirst module 200 by the air flow) that is equal to the width W of thefirst module 300 and double the width W of the second module 200.

The length L of the third module 400, in the parallel direction to theadvancement direction of the air flow along the first module 200, in thesecond embodiment can be less than the above-mentioned dimension W and,for example substantially equal to the length L of the second module300.

The third module 400, the second module 300 and the first module 200exhibit a same height, for example a maximum length of the internalcompartment of a container of standard dimensions, for exampletransportable by sea.

In practice, in the second embodiment, the apparatus 10 is constitutedby two first modules 200, two second modules 300, two third modules 400,fixed to one another as described above.

One of the second modules 300 exhibits one of the fixed interconnectingfaces (as described above for the first embodiment) to theinterconnecting face of each of the two first modules 200.

In practice, each interconnecting ace of a first module 200 occupies(and is fixed) to half the surface of the interconnecting face of one ofthe second modules 300.

The first modules 200 are fixed to one another by a respectivecontiguous lateral face, for example they can be fixed to one another bybolts or another threaded organ and/or by means of appropriate weldseams which interconnect the cross members 202 defining the contiguouslateral faces.

The further interconnecting face of the second module 300 opposite theface fixed to the first modules 200, is fixed to the interconnectingface of the further second module 300. The interconnecting faces of thetwo second modules 300 can be fixed to one another by bolts or anotherthreaded organ and/or by means of appropriate weld seams whichinterconnect the longitudinal members defining the portals 301 of thesecond modules 300.

The further interconnecting face of the second module 300 opposite theface fixed to the second module 300, is fixed to the interconnectingface of the third module 400.

The interconnecting faces of the third module 400 and the second module300 can be fixed to one another by bolts or another threaded organand/or by means of appropriate weld seams which interconnect thelongitudinal members defining the portals 301 of the further secondmodule 300 and the portals 401 of the third module 400.

Each refrigerating unit 30 of each second module 300 is connected, asdescribed in the foregoing, to each heat exchange plate 24 of one of thetwo condensation units 20.

In the second embodiment, a converging nozzle 230 is connected to eachventilator 23 of the condensation unit 20 more distant from therespective refrigerating unit 30 (and respect second module 300), sothat the dehumidified air exiting from the first module 200 isaccelerated and sent on towards the more distant second module 300.

Obviously the purification plant 40 will receive the water to bepurified from each collecting tub 291,292,293 of each condensation unit20.

In a third embodiment shown in FIG. 11, in which the above-describedwater flow and the power of the apparatus 10 are substantially doublewith respect to the apparatus 10 of the second embodiment, the thirdmodule 400 exhibits a width, for example defined by the extension of ashort side (horizontal) of the front portal 401 (in relation to thecrossing direction of the first module 200 by the air flow), whichextension is W, in which W is for example a maximum width of theinternal compartment of a container of standard dimensions (for example234 cm), for example transportable by sea.

In practice, in the third embodiment, the third module 400 exhibits awidth W (in the transversal direction to the crossing direction of thefirst module 200 by the air flow) that is equal to the width W of thesecond module 300 and double the width W of the first module 200.

The length L of the third module 400, in the parallel direction to theadvancement direction of the air flow along the first module 200, in thesecond embodiment can be less than the above-mentioned dimension W and,for example substantially equal to the length L of the second module300.

The third module 400 and the first module 200 exhibit a same height, forexample a maximum length of the internal compartment of a container ofstandard dimensions, for example transportable by sea.

In practice, in the third embodiment, the apparatus 10 is constituted byfour first modules 200, four second modules 300, and at least one, forexample two third modules.

In this embodiment, two third modules are fixed to one another by meansof a respective interconnecting face, for example by bolts or anotherthreaded organ and/or by means of appropriate weld seams whichinterconnect the longitudinal members defining the portals 401 of thethird modules 300

As described above in relation to the second embodiment, two respectivesecond modules 300 are joined and fixed to both interconnecting freefaces of the third modules 400 (opposite the interconnecting facejoining the third modules) to faxes of which free interconnecting facesfurther interconnecting faces of two further second modules 300 arerespectively fixed.

As described above in relation to the second embodiment, twointerconnecting faces of two first modules 200 are respectively fixed toeach free interconnecting surface of the second modules 300, which twointerconnecting faces are fixed to one another by two contiguous lateralfaces, as described in the foregoing for the second embodiment.

In practice, in the third embodiment, the apparatus 10 exhibits asymmetrical distribution of the first and second modules 200, 300 withrespect to a perpendicular plane to the air flow advancement direction,along the first modules 200 and passing through the contact planebetween the two third modules 400.

In this case too, each refrigerating unit 30 of each second module 300is connected, as described in the foregoing for the second embodiment,to each heat exchange plate 24 of one of the two condensation units 20.

In the second embodiment, a converging nozzle 230 is connected to eachventilator 23 of the condensation unit 20 most distant from therespective refrigerating unit 30 (and respect second module 300), sothat the dehumidified air exiting from the first module 200 isaccelerated and sent on towards the most distant second module 300.

Obviously each purification plant 40 arranged in the respective thirdmodule 400 will receive the water to be purified from each collectingtub 291,292,293 of each closest condensation unit 20.

For example, the first, second and third module 200, 300, 400, oncefixed reciprocally as described in the foregoing define a substantiallysingle-block apparatus having a width W of slightly less than themaximum width of the internal compartment of a container of standarddimensions (for example 220 cm), for example transportable by sea; aheight of slightly less than the maximum height of the internalcompartment of a container of standard dimensions (for example 263 cm),for example transportable by sea, and having a variable length as afunction of the flow rate and/or power requested, which is substantially495 cm for the first embodiment, 905 cm for the second embodiment and1810 cm for the third embodiment, so as to be able to be inserted in astandard container for transportation thereof.

Functioning of the Apparatus

In the normal functioning of the apparatus 10, the ventilators 23 areset in operation so as to generate a continuous air flow that crossesthe condensation unit 20, in particular the heat exchange plate 24 andthe heat exchangers 25 and 26.

At the same time, the compressor 310 and the condenser 312 of therefrigerating unit 30 are also set in operation, so that the evaporationof the refrigerating unit in the heat exchange plate 24 is able to coolthe air flow to a lower temperature than the dew point temperature, thuscausing condensing of the vapor in the air flow, which vapor accumulatesin the form of water in the collecting tub 291 and is then sent on tothe purification unit 40.

At the same time the recycling pump 256 is also set in operation, so asto cause the heat exchange liquid to flow internally of the closedhydraulic circuit 255 connecting the heat exchangers 25 and 26. In thisway, the cold and dehumidified air flow exiting the heat exchange plate24 cools the heat exchange liquid which is in the second exchanger 26.This cold liquid is sent upstream of the first exchanger 25 where it isheated by the air flow in inlet before returning back to the secondexchanger 26. In this way, the air flow crossing the first exchanger 25is pre-cooled before reaching the heat exchange plate 24. Owing to thispre-cooling, the air flow can be brought to a temperature equal to ornear to the dew point, without using energy directly produced by therefrigerating unit 30, but simply by recuperating a part of the heatenergy which otherwise would be lost in the air.

Note here that the vapor in the air flow can condensate not only in theheat exchange plate 24 but also in part in the first heat exchanger 25.The water produced in the first heat exchanger 25 accumulates in therelative collecting tub 292 and is thence also sent on to thepurification unit 40.

The cold and dehumidified air flow that exits the condensation unit 20,downstream of the ventilators 23, can be conveyed into the refrigeratingunit 30, so as to pass it through the condenser 312, where it can coolthe refrigerating fluid in the gaseous state by means of the heatexchange plate 24, causing condensation thereof.

Alternatively, the cold and dehumidified cold air flow from thecondensation unit 20, or a part thereof, can be deviated and conveyedtowards other users. For example, the air flow can be used for supplyingother air treatment plants and/or for supply conditioning/cooling plantsof buildings or other structures.

In these and other cases, the condenser 312 of the refrigerating unit 30can be supplied wholly or in part by a second flow of ambient air comingdirectly from outside the plant 10, for example entering by the accessopening of the second module 300. As mentioned in the foregoing, it ispreferable for a mixture of air substantially comprising ⅔ of ambientair and ⅓ of cold and dehumidified air coming from the condensation unit20 to be made to cross the condenser 312.

With the aim of making this functioning effective, all the activecomponents of the apparatus 10, such as for example the compressor 310,the condenser 312 and the expansion valve 310 of the refrigerating unit30, as well as the heat exchange plate 24 and the heat exchangers 25 and26 and the ventilators of the condensation unit 20, are generallydimensioned so as to obtain a certain water production in determinedstandard environmental conditions. For example, the plant 10 can bedimensioned so as to obtain about 100 liters of water per hour, instandard atmospheric conditions, i.e. with ambient air at temperaturesof about 30° C. and relative humidity at about 70%.

In order to obtain these performances in standard atmosphericconditions, the refrigerating unit 30 can be made to function so thatthe saturated vapor temperature of the refrigerating fluid is about 5.5°C. (at the compressor 310 inlet), while the ventilators 23 of thecondensation unit 20 can be made to function at a predefined velocityable to generate an air flow of about 8000 m³/h.

During the above-described functioning, the apparatus 10 can also beused to heat the vector fluid which circulates in the auxiliary circuit326, which (as mentioned) can in turn be used internally of a heatingplant or as hot sanitary water.

In this case, the intercept valve 324 and possibly the intercept valve325 is regulated so that the refrigerating fluid at high temperaturecoming from the compressor 310 can flow into the second condenser 321.In particular the refrigerating fluid can be entirely deviated into thesecond condenser 321, completely bypassing the condenser 312. In thisway, a total recuperation of the condensation heat generated by thepreceding compression of the refrigerating fluid is obtained in thesecond condenser, which heats the vector fluid of the auxiliary circuit326.

As mentioned in the foregoing, the hot vector fluid obtained in thesecond condenser 321 might be used for defrosting the heat exchangeplate 24 and, for example, also the heat exchangers 25 and 26. This needcan be manifested when the plant 10 is used for production of waterstarting from air having a dew point temperature of less than 0° C. Inthese climatic conditions, as the air condensation point is lower thanthe water freezing point, ice can be directly obtained whichprogressively accumulates on the tubes of the tube bundle 244 of theheat exchange plate 24. In these cases, while the apparatus 10 functionsto produce water/ice, the refrigerating fluid coming from the condenser310 is deviated into the second condenser 321, so as to heat the vectorfluid in the storage tank 328. By opening appropriate valves in theauxiliary circuit 326, the vector fluid accumulated can then becyclically sent to the tube bundle 330 which is internal of the heatexchange plate 24, obtaining thawing of the ice and therefore theproduction of water which accumulates in the respective collecting tub291,292,293. In particular, the frequency with which the hot vectorfluid is sent to the tube bundle 330 can be regulated by a centralcontrol unit on the basis of the temperature of the air flow in outletfrom the condensation unit 20.

As with the reduction of the air temperature it is progressively moredifficult to thaw the ice, this operation can be accelerated and mademore efficient, enabling the hot vector fluid of the storage tank 328 tocirculate also in the hydraulic circuit 255, so that the heat exchangers25 and 26 in fact become heating elements that effectively aid thethawing of the ice.

The invention as it is conceived is susceptible to numerousmodifications, all falling within the scope of the inventive concept.

Further, all the details can be replaced with othertechnically-equivalent elements.

In practice the materials used, as well as the contingent shapes anddimensions, can be any according to requirements, without forsaking thescope of protection of the following claims.

1. A modular apparatus (10) for water production from atmospheric airwhich comprises: a first parallelepiped module (200) provided with aninlet opening (21) for moist air, an outlet opening (22) of thedehumidified air, a ventilator (23), configured such as to force an airflow to cross an internal volume of the first module (200) from theinlet opening (21) to the outlet opening (22), a condensation unit (20),located internally of the first module (200) so as to intercept the airflow, and a collecting tub (291, 292, 293) located inferiorly of thecondensation unit (20) for collecting condensation water that isseparating from the air flow; and a second parallelepiped module (300)in which a refrigerating unit (30) is contained, provided with at leasta portion of a refrigerating circuit (31) in which a cooling fluidcirculates, and an evaporator, which is contained in the firstparallelepiped module (200), in which the cooling fluid evaporates so asto cool the air flow internally of the condensation unit (20); whereinthe first module (200) and the second module (300) are fixed to oneanother at a respective interconnecting face and wherein the secondmodule (300) exhibits a side of the interconnecting face having a width(W) that is twice a width (W/2) of a side of the interconnecting face ofthe first module (200).
 2. The apparatus (10) of claim 1, wherein theoutlet opening (22) is arranged at the interconnecting face of the firstmodule (200) and the inlet opening (21) is made at an opposite face ofthe interconnecting face of the first module (200).
 3. The apparatus(10) of claim 1 further comprising a third parallelepiped module (400)in which a water purification unit (40) of the condensed water iscontained, configured so as to collect the water from the collectingtube (291, 292, 293), wherein the third module (400) and the secondmodule (300) are fixed to one another at a respective interconnectingface and wherein the second module (300) exhibits a side of theinterconnecting face having a width (W) that is twice a width (W/2) of aside of the interconnecting face of the first module (400).
 4. Theapparatus (10) of claim 3, wherein a contiguous face to theinterconnecting face of the third module (400) is provided with a sideexhibiting a length (L) equal to a length (L) of a side of a contiguousface to the interconnecting face of the first module (200), the firstmodule (200) and the second module (300) being reciprocally flanked andfixed by means of the respective contiguous faces.
 5. The apparatus (10)of claim 1 further comprising a third parallelepiped module (400) inwhich a water purification unit (40) of the condensed water iscontained, configured so as to collect the water from the collectingtube (291, 292, 293), wherein the third module (400) and the secondmodule (300) are fixed to one another at a respective interconnectingface and wherein the second module (300) exhibits a side of theinterconnecting face having a width (W) that is equal to a width (W) ofa side of the interconnecting face of the third module (400).
 6. Theapparatus (10) of claim 5, further comprising a pair of the firstmodules (200) flanked and fixed reciprocally via a respective contiguousface to the interconnecting face, respectively fixed to theinterconnecting face of a second module (300) of a pair of the secondmodules (400) fixed to one another via an opposite face with respect tothe respective interconnecting face.
 7. The apparatus (10) of claim 5further comprising two pairs of first modules (200) and two pairs ofsecond modules (300), wherein the inlet openings (21) of the firstmodules (200) of a first pair of first modules (200) are symmetricallyopposite the inlet openings (21) of the first modules of the second pairof first modules (200).
 8. The apparatus of claim 6, wherein therefrigerating unit (30) of each of the second modules (300) is providedwith a respective branch tube or conduit configured to cross arespective condensation unit (20) located in a first module (200) of thefirst modules.
 9. The apparatus (10) of claim 6, wherein the outletopenings (22) of one or the first modules (200) comprises an acceleratorelement (230) of the dehumidified air flow which exits from the outletopening.
 10. The apparatus (10) of claim 1, wherein a pair of heatexchangers (25,26), of which a first heat exchanger (25) and a secondheat exchanger (26), are contained in each first module (200),respectively located upstream and downstream of the condensation unit(20) in the crossing direction thereof by the air flow, the pair of heatexchangers (25,26) being connected by means of a hydraulic circuit (255)comprising a recycling pump (256) of a liquid contained in the hydrauliccircuit (255).
 11. The apparatus (10) of claim 1, wherein therefrigerating circuit (31) comprises a compressor (310) of the coolingfluid moved by a motor (311), a condenser (312) of the cooling fluidlocated downstream of the compressor (310) in the circulating directionof the cooling fluid in the refrigerating circuit (31), an expansionvalve (313) located downstream of the condenser and the evaporator ofthe cooling fluid.
 12. The apparatus (10) of claim 11, wherein thecondensation unit (20) is the evaporator of the refrigerating circuit.13. The apparatus (10) of claim 11, wherein the condenser (312)comprises a dissipating fan (314) located on an upper face of the secondmodule (300), a lateral faces contiguous to an interconnecting face ofthe second module (300) exhibiting an access opening for the ambientair.
 14. The apparatus (10) of claim 13, wherein a size of the accessopening, the ventilator (23) and the dissipating fan (314) areconfigured so as to define an air mixture substantially comprising ⅔ ofambient air entering the second module (300) from the access opening and⅓ of dehumidified air entering the second module (300) by means of theventilator (23).
 15. The apparatus (10) of claim 11, wherein the motor(311) is an electric motor.
 16. The apparatus (10) of claim 1, whereinthe first module (200) is provided with a filter apparatus (27)configured to be crossed by the whole moist air flow which enters theinlet opening (21).
 17. The apparatus (10) of claim 3, wherein the waterpurification unit (40) comprises at least an anti-particulate filter anda mineralizer.
 18. The apparatus (10) of claim 3, wherein the waterpurification unit (40) comprises at least a sterilizer.